Reduced pivot center distance assembly for a railway car

ABSTRACT

A reduced pivot center distance system for a railway car in which each end of the load is supported on a bolster carried by the running gear by means of an arcuate sliding connection comprising an arcuate way and an arcuate slide disposed in the way and connected to the load so as to constrain the load to swing about a pivot point which is the center of the arc of movement of the sliding connection. Preferably the arcuate sliding connection is supported on the bolster for lateral sliding movement to permit lateral shifting of the entire load if necessary.

[ 51 Sept. 24, 1974 REDUCED PIVOT CENTER DISTANCE ASSEMBLY FOR A RAILWAY CAR [75] Inventor:

[73] Assignee: Norca Machinery Corporation, New

York, NY.

[22] Filed: Dec. 29, 1971 [21] Appl. No.: 213,480

Franco Fedele, Florence, Italy [52] US. Cl. 105/367, 105/159 [51] Int. Cl B6111 3/16 [58] Field of Search i. 105/367, 159

[56] References Cited UNITED STATES PATENTS 3,532,061 10/1970 Bohm 105/367 FOREIGN PATENTS OR APPLICATIONS 1,057,638 5/1959 Germany 105/367 1,195,794 7/1965 Germany 105/367 Primary ExaminerDrayton E. Hoffman Attorney, Agent, or Firm-Shenier & OConnor [5 7 ABSTRACT A reduced pivot center distance system for a railway car in which each end of the load is supported on a bolster carried by the running gear by means of an arcuate sliding connection comprising an arcuate way and an arcuate slide disposed in the way and connected to the load so as to constrain the load to swing about a pivot point which is the center of the arc of movement of the sliding connection. Preferably the arcuate sliding connection is supported on the bolster for lateral sliding movement to permit lateral shifting of the entire load if necessary.

16 Claims, 6 Drawing Figures PAIENIE SEPZ 41874 sum 1 or 4 QM QM INVENTOR. Fea e/e Emma BY 7 H T TORNEYS INVENTOR. Franco Fade/e I BY I zm srm ear 4 QQ QQJJ PAIENIED 35 241914 HTTORNEYS PAIENIEUSEPZMBH SHEET 3 [IF INVENTOR. Franco Ede/e A T TORNEYS PAIENIEB EPM 3. e37; 295 saw u or 4 INVENTOR. Evnea Ede/e 6 T YORNE Y5 REDUCED PIVOT CENTER DISTANCE ASSEMBLY FOR A RAILWAY CAR BACKGROUND OF THE INVENTION In the conventional railway load supporting system the load is pivotally carried on spaced wheel trucks at load support centers so that when the train negotiates a curve the trucks pivot relative to the load at the support centers. When extremely long loads, such as large electrical transformers and bridge beams, are transported by rail, the load is supported adjacent its ends between relatively widely-separated sets of running gear. While such an arrangement is satisfactory under normal straight running conditions when the load must negotiate a relatively sharp curve the load swings inboard for such a distance that it will either strike a wayside obstacle or it will be unable to negotiate the curve.

Various schemes have been proposed in the prior art for overcoming the problem outlined above of enabling long and wide loads to negotiate curves without striking roadside obstacles. It has, for example, been suggested that removable pins can be inserted through the supporting beams and into the running gear at points inboard of the support centers to cause the load to swing around pivot centers separated by a lesser distance than are the load support centers. The difficulty involved in such an arrangement is that the pivot pins are not sufficiently stout to withstand the shear forces involved in ordinary train operation owing to the accordion effect. Secondly, this is a manual operation which must be anticipated and which must be performed while the train is stopped before the curve is negotiated.

Another arrangement which has been proposed is to provide a surface on the running gear bolster to which the load is applied and which permits sliding or rolling movement between the member carrying the load and the bolster surface. In such an arrangement, there is provided a rigid beam connecting the member applying the load to a pin or the like at the point on the bolster inboard of the load point at which it is desired to have the load pivot. While such an arrangement has the advantage of not requiring a manual operation in order to provide the reduced pivot center distance, it has the disadvantage that the pivot connection must absorb the relatively large forces incident to normal operation of the train.

I have invented a reduced pivot center distance assembly for a railway car or the like which overcomes the problems outlined hereinabove. My assembly enables a railway car or the like carrying a very long load to negotiate a curve without striking roadside obstructions. My assembly easily absorbs the thrust forces incident to normal operation ofa train. My assembly facilitates the operation of shifting the entire load laterally if necessary.

SUMMARY OF THE INVENTION One object of my invention is to provide an improved reduced pivot center distance assembly for railway cars and the like.

Another object of my invention is to provide an improved reduced pivot center distance assembly which does not require a manual operation to put it in use.

Yet another object of my invention is to provide an improved reduced pivot center distance assembly which can easily accommodate the thrust forces incident to normal operation of a train.

A further object of my invention is to provide an improved reduced pivot center distance assembly which facilitates lateral shifting of the entire load.

Other and further objects of my invention will appear in the following description.

In general, my invention contemplates the provision of an improved reduced pivot center distance assembly for railway cars and the like in which each end of the load is supported on a bolster on the running gear by means of an arcuate sliding connection comprising an arcuate slide disposed in an arcuate way formed in a lateral slide supported in a transverse way carried by the bolster with the arc of curvature of the arcuate slide having a center at the point at which the load pivots with respect to the bolster.

BRIEF DESCRIPTION OF THE DRAWINGS In the accompanying drawings which form part of the instant specification and which are to be read in conjunction therewith and in which like reference numerals are used to indicate like parts in the various views:

FIG. 1 is a side elevation of a railway car and load incorporating my improved reduced pivot center distance assembly.

FIG. 2 is a top plan view of a railway car or the like including my improved reduced pivot center distance assembly while negotiating a curve.

FIG. 3 is a fragmentary side elevation of a car provided with my improved reduced pivot center distance assembly with parts broken away and with other parts shown in section.

FIG. 4 is a fragmentary top plan view of a railway car provided with my improved reduced pivot center distance assembly with parts broken away and with other parts shown in section.

FIG. 5 is a top plan view of my improved reduced pivot center distance assembly with parts removed.

FIG. 6 is a top plan view of my improved reduced pivot distance assembly with parts removed and with other parts broken away.

DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to the drawings, a railway car or the like, indicated generally by the reference character 10, of the special type which incorporates my improved reduced pivot center distance assembly, is adapted to ride over tracks 12 and 14 and past a roadside obstruction such, for example, as a building 16. The load 18 on the car 10 is unusually long and wide so that it cannot be shipped on the ordinary railway flatcar. One example of such an item is a large electrical transformer. Another example would be a large steel girder for use in constructing a bridge or the like. In the car 10 the load 18 rests on a carrier 20 which is supported between a forward car section indicated generally by the reference character 22 and a rear or after car section indicated generally by the reference character 24 assuming that the train is moving in the direction from right to left in FIG. 1.

Since each of the forward and after car sections 22 and 24 are substantially identical, only one of them will be described in detail. The after section 24 includes forward and after sets of running gear indicated generally respectively by the reference character 26 and 28. Running gear 26 includes a six-wheel truck 30 and a four-wheel truck 32 which trucks support a forward lower bolster 34. The running gear 28 includes a sixwheel truck 36 and a four-wheel truck 38 which trucks carry an after lower bolster 40. The two lower bolsters 34 and 40, carry the main or span bolster 42 of the section 24.

The load supporting reduced pivot center distance and lateral shifting assembly structure indicated generally by the reference character 44 of the section 24 includes spaced triangular beams 46 and 48 the lower left hand corner of each of which are viewed in FIG. 3 is provided with a bearing opening 50 for receiving a hinge pin 52 which couples the beams to the support 20. Respective pairs of compression jacks 54 have rods 56 connected to pads 58 which are adapted to be moved into engagement with the ends of the load 18 so as to position the load on the support 20.

A plurality of transversely extending guide rods 60 and 62 and 64 are received in pairs of guides 66, 68 and 70 on the respective beams 46 and 48 to permit the lateral spacing between the beams to be adjusted to the load size between a minimum distance indicated by the broken lines in FIG. 4 and the maximum distance indicated by the full lines in the FIGURE.

The right end of each of the beams 46 as viewed in FIGS. 3 and 4 is formed with an opening 72 for receiv ing a pivot pin 74 the center of which carries a center fulcrum 76. Fulcrum 76 is formed with a groove 78 extending axially of pin 74 in the underside of the fulcrum. A tongue 80 on a cradle shoe 82 is disposed in the slot 78. Cradle shoe 82 rests on a fulcrum guide 84. Guide 84 also receives end fulcrums 86 carried by the pivot pin 74. I mount guide 84 on a pivot bolster 90.

My assembly further includes an arcuate guide 92 carried by the underside of a plate 94 adapted to be secured to the underside of bolster 90 by bolts or the like passing through bolt-holes 96 in plate 94. Guide 92 is received in an arcuate way 98 formed in a lateral slide 100 and is retained therein by any suitable means such as by keys 102. Lateral slide 100, in turn, is disposed in a transverse way 104 formed in a guide 106. Keys 108 retain the lateral slide 100 in the way 104. Any suitable means, such for example, as bolts 110 secure the guide 106 to the bolster 42. It will be appreciated that the guide 92 on way 98 constrains the load 18 to pivot relative to bolster 42 around a point at the center of the radius of curvature of guide 92. Further, slide 100 and way 104 permit lateral transverse movement of the load relative to bolster 42 in a manner to be described. It is to be noted also that I may coat the surface of guide 92 and of way 98 with polytetrafluoroethylene to minimize friction. I may do the same with slide 100 and way 104.

A reduced pivot beam 112 having a slot 114 in the apex thereof receives a pivot pin 116 to be described more fully hereinafter. Bolts 118 secure the legs of the beam 112 to the bolster 90. As will be more fully pointed out hereinafter, I am able to use the pin 116 and slot 114 connection between the reduced pivot beam and the point around which the load pivots since pin 116 is not required to take any thrust. I provide beam 112 in order to maintain the alignment between the pivot center which is on the axis of pin 116 and the point at which the load is applied to the bolster 90. In this way, I minimize the possibility of jamming the arcuate guide 92 in its way 98.

Respective spaced struts 120 and 122 making up a lateral shifting beam structure extend between respective double-acting cylinders 124 and 126 the rods of which are secured to the bolster 42. Any suitable means such, for example, as bolts 134 may be employed to secure the struts 120 and 122 to cylinder 124. Bolts 136 connect the other ends of the struts 120 and 122 both to the cylinder 126 and to the lateral slide 100. Bolts 138 connect the slide to the cylinder 128.

In operation of my improved reduced pivot center distance assembly the car 10 including the two sections 22 and 24 normally supports the load at load centers S and S separated by a distance D,. When the train is moving straight the longitudinal axis of the two sections 22 and 24 is aligned with the longitudinal axis of the two sets of running gear 26 and 28. When the train negotiates a curve owing to the radius of curvature of the curved guides 92 the load pivots with relation to car sections 22 and 24 about points P and P, each of which is located at the center of the radius of curvature of the associated guide 92. As can be seen by reference to FIG. 1, the points P and P are separated by a shorter distance than are the points S and S. Owing to that fact, roadside obstructions such as the building 16 are avoided as illustrated in FIG. 2. In that FIGURE I have indicated the position the load would occupy if constrained to pivot around points S and S' in broken lines. It will be clear that in such a position it would strike the building 16 as it rounded the curve. In pivoting around points P and P as indicated by the full lines, it will clear the obstacle.

In some rare instances it becomes necessary to shift the entire load laterally of the running gear in one direction or the other to clear an obstacle. When this becomes necessary fluid under pressure is supplied to corresponding sides of cylinders 124, 126 and 128 to cause them to shift the beam made up of struts 120 and 122 and thus to shift pivot pins 116, the slides and the entire load 18 laterally of the running gear in the required direction. This is achieved without interfering with the operation of the reduced pivot center distance assembly.

It will be seen that I have accomplished the objects of my invention. l have provided an improved reduced pivot center distance assembly for railway cars or the like which overcomes the defects of assemblies of the prior art intended to accomplish the same result. My assembly does not require a manual operation to place it in operating condition. It easily absorbs thrust forces incident to normal train operation. It facilitates lateral shifting of the entire load.

It will be understood that certain features and subcombinations are of utility and may be employed without reference to other features and subcombinations. This is contemplated by and is within the scope of my claims. It is further obvious that various changes may be made in details within the scope of my claims without departing from the spirit of my invention. It is, therefore, to be understood that my invention is not to be limited to the specific details shown and described.

Having thus described my invention, what I claim is:

1. An assembly for supporting a load for movement along a way including in combination, a truck having wheels adapted to move along said way, a member for receiving said load on a load support center, an arcuate slide carried by one of said member and said truck at a location spaced from said load support center, and means forming an arcuate way on the other of said member and said truck at said location for receiving said slide for sliding movement therein to constrain said member to pivot relative to said truck about a pivot center spaced from said load suport center while resisting thrust forces generally in the direction of said way.

2. An assembly as in claim 1 including means for constraining said way forming means to move rectilinearly transversely of said truck.

3. An assembly as in claim 2 in which said arcuate way forming means is a rectangular slide and in which said way constraining means comprises said rectangular slide and means forming a rectangular way for receiving said rectangular slide.

4. An assembly as in claim 1 in which said slide has a central radius of curvature equal to the distance between said pivot center and said load support center.

5. An assembly as in claim 4 in which said slide is carried by said member and in which said way is on said truck.

6. An assembly as in claim 5 including a pivot pin at said pivot center and a beam extending between said pivot pin and said member.

7. An assembly as in claim 6 in which said beam is formed with a slot for receiving said pin.

8. An assmbly as in claim 3 including actuatable means for moving said rectangular slide relative to said rectangular way to move said support point laterally relative to said truck.

9. A car assembly for supporting an elongated load for movement along a way including in combination, spaced truck assemblies adapted to move along said way, respective members carried by said trucks for applying said load to said trucks at load support centers spaced by a certain distance, respective arcuate slides carried by respective first ones of said members and said trucks and spaced by a distance less than said certain distance, and respective means forming arcuate ways on respective other ones of said members and said trucks and spaced by said lesser distance to receive the respective ways for sliding movement therein to constrain said members to pivot relative to the associated trucks about pivot centers spaced by said lesser distance while resisting thrust forces generally in the direction of said way.

10. An assembly as in claim 9 in which each of said arcuate way forming means is a rectangular slide, and in which said assembly includes respective means forming rectangular ways for receiving said rectangular slides.

11. An assembly as in claim 9 in which each of said slides has a central radius of curvature equal to the distance between its associated pivot center and the corresponding load support center.

12. An assembly as in claim 11 in which each slide is carried by its associated member and in which each way is on the corresponding truck.

13. An assembly as in claim 12 including respective pivot pins at said pivot centers and respective beams between said pivot pins and said members.

14. In a reduced pivot center distance railway car, an assembly including a truck having a longitudinal centerline, means on said truck forming a way extending generally transversely of said centerline, a rectangular slide received in said way, means forming an arcuate way in said rectangular slide, said arcuate way having a center radius emanating from a pivot center, an arcuate slide received in said arcuate way, and means for applying a load to said arcuate way about a load center spaced from said pivot center.

15. An assembly as in claim 14 in which said load applying means comprises means forming a fulcrum.

16. An assembly as in claim 14 including means for concomitantly shifting said rectangular slide and said pivot center. 

1. An assembly for supporting a load for movement along a way including in combination, a truck having wheels adapted to move along said way, a member for receiving said load on a load support center, an arcuate slide carried by one of said member and said truck at a location spaced from said load support center, and means forming an arcuate way on the other of said member and said truck at said location for receiving said slide for sliding movement therein to constrain said member to pivot relative to said truck about a pivot center spaced from said load suport center while resisting thrust forces generally in the direction of said way.
 2. An assembly as in claim 1 including means for constraining said way forming means to move rectilinearly transversely of said truck.
 3. An assembly as in claim 2 in which said arcuate way forming means is a rectangular slide and in which said way constraining means comprises said rectangular slide and means forming a rectangular way for receiving said rectangular slide.
 4. An assembly as in claim 1 in which said slide has a central radius of curvature equal to the distance between said pivot center and said load support center.
 5. An assembly as in claim 4 in which said slide is carried by said member and in which said way is on said truck.
 6. An assembly as in claim 5 including a pivot pin at said pivot center and a beam extending between said pivot pin and said member.
 7. An assembly as in claim 6 in which said beam is formed with a slot for receiving said pin.
 8. An assmbly as in claim 3 including actuatable means for moving said rectangular slide relative to said rectangular way to move said support point laterally relative to said truck.
 9. A car assembly for supporting an elongated load for movement along a way including in combinaTion, spaced truck assemblies adapted to move along said way, respective members carried by said trucks for applying said load to said trucks at load support centers spaced by a certain distance, respective arcuate slides carried by respective first ones of said members and said trucks and spaced by a distance less than said certain distance, and respective means forming arcuate ways on respective other ones of said members and said trucks and spaced by said lesser distance to receive the respective ways for sliding movement therein to constrain said members to pivot relative to the associated trucks about pivot centers spaced by said lesser distance while resisting thrust forces generally in the direction of said way.
 10. An assembly as in claim 9 in which each of said arcuate way forming means is a rectangular slide, and in which said assembly includes respective means forming rectangular ways for receiving said rectangular slides.
 11. An assembly as in claim 9 in which each of said slides has a central radius of curvature equal to the distance between its associated pivot center and the corresponding load support center.
 12. An assembly as in claim 11 in which each slide is carried by its associated member and in which each way is on the corresponding truck.
 13. An assembly as in claim 12 including respective pivot pins at said pivot centers and respective beams between said pivot pins and said members.
 14. In a reduced pivot center distance railway car, an assembly including a truck having a longitudinal centerline, means on said truck forming a way extending generally transversely of said centerline, a rectangular slide received in said way, means forming an arcuate way in said rectangular slide, said arcuate way having a center radius emanating from a pivot center, an arcuate slide received in said arcuate way, and means for applying a load to said arcuate way about a load center spaced from said pivot center.
 15. An assembly as in claim 14 in which said load applying means comprises means forming a fulcrum.
 16. An assembly as in claim 14 including means for concomitantly shifting said rectangular slide and said pivot center. 